EP3830444B1 - Amortisseur hydraulique à amortissement variable pour suspension de véhicule - Google Patents
Amortisseur hydraulique à amortissement variable pour suspension de véhicule Download PDFInfo
- Publication number
- EP3830444B1 EP3830444B1 EP19758811.4A EP19758811A EP3830444B1 EP 3830444 B1 EP3830444 B1 EP 3830444B1 EP 19758811 A EP19758811 A EP 19758811A EP 3830444 B1 EP3830444 B1 EP 3830444B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- chamber
- valve
- shock
- rebound
- absorber
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Active
Links
- 239000006096 absorbing agent Substances 0.000 title claims description 62
- 238000013016 damping Methods 0.000 title claims description 39
- 239000000725 suspension Substances 0.000 title description 3
- 230000006835 compression Effects 0.000 claims description 73
- 238000007906 compression Methods 0.000 claims description 73
- 239000012530 fluid Substances 0.000 claims description 28
- 230000000694 effects Effects 0.000 description 2
- 230000001419 dependent effect Effects 0.000 description 1
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/10—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium using liquid only; using a fluid of which the nature is immaterial
- F16F9/14—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect
- F16F9/16—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect involving only straight-line movement of the effective parts
- F16F9/18—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect involving only straight-line movement of the effective parts with a closed cylinder and a piston separating two or more working spaces therein
- F16F9/185—Bitubular units
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/34—Special valve constructions; Shape or construction of throttling passages
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/44—Means on or in the damper for manual or non-automatic adjustment; such means combined with temperature correction
- F16F9/46—Means on or in the damper for manual or non-automatic adjustment; such means combined with temperature correction allowing control from a distance, i.e. location of means for control input being remote from site of valves, e.g. on damper external wall
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/50—Special means providing automatic damping adjustment, i.e. self-adjustment of damping by particular sliding movements of a valve element, other than flexions or displacement of valve discs; Special means providing self-adjustment of spring characteristics
- F16F9/516—Special means providing automatic damping adjustment, i.e. self-adjustment of damping by particular sliding movements of a valve element, other than flexions or displacement of valve discs; Special means providing self-adjustment of spring characteristics resulting in the damping effects during contraction being different from the damping effects during extension, i.e. responsive to the direction of movement
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G13/00—Resilient suspensions characterised by arrangement, location or type of vibration dampers
- B60G13/02—Resilient suspensions characterised by arrangement, location or type of vibration dampers having dampers dissipating energy, e.g. frictionally
- B60G13/06—Resilient suspensions characterised by arrangement, location or type of vibration dampers having dampers dissipating energy, e.g. frictionally of fluid type
- B60G13/08—Resilient suspensions characterised by arrangement, location or type of vibration dampers having dampers dissipating energy, e.g. frictionally of fluid type hydraulic
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G2202/00—Indexing codes relating to the type of spring, damper or actuator
- B60G2202/20—Type of damper
- B60G2202/24—Fluid damper
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G2204/00—Indexing codes related to suspensions per se or to auxiliary parts
- B60G2204/62—Adjustable continuously, e.g. during driving
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G2206/00—Indexing codes related to the manufacturing of suspensions: constructional features, the materials used, procedures or tools
- B60G2206/01—Constructional features of suspension elements, e.g. arms, dampers, springs
- B60G2206/40—Constructional features of dampers and/or springs
- B60G2206/41—Dampers
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G2500/00—Indexing codes relating to the regulated action or device
- B60G2500/10—Damping action or damper
- B60G2500/104—Damping action or damper continuous
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G2500/00—Indexing codes relating to the regulated action or device
- B60G2500/10—Damping action or damper
- B60G2500/11—Damping valves
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G2800/00—Indexing codes relating to the type of movement or to the condition of the vehicle and to the end result to be achieved by the control action
- B60G2800/16—Running
- B60G2800/162—Reducing road induced vibrations
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F2222/00—Special physical effects, e.g. nature of damping effects
- F16F2222/12—Fluid damping
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F2228/00—Functional characteristics, e.g. variability, frequency-dependence
- F16F2228/06—Stiffness
- F16F2228/066—Variable stiffness
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F2232/00—Nature of movement
- F16F2232/08—Linear
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F2234/00—Shape
- F16F2234/02—Shape cylindrical
Definitions
- the present invention relates to a variable-damping hydraulic shock-absorber, particularly for use in a vehicle suspension, as specified in the preamble of independent claim 1.
- variable-damping hydraulic shock-1 absorber comprising a pair of electronically-controlled valves, made for example as solenoid valves, one of which is arranged to adjust the flow of the damping fluid (typically oil) of the shock-absorber during the compression phase only, while the other is arranged to adjust the flow of the damping fluid during the rebound (or extension) phase only.
- damping fluid typically oil
- shock-absorber of the above-mentioned type is known for example from DE 10 2005 053 394 A1 .
- the shock-absorber comprises an outer cylindrical tube, an inner cylindrical tube coaxial to the outer cylindrical tube and defining with the latter a reservoir chamber, a rod which is arranged coaxially to the two cylindrical tubes and partially protrudes therefrom, and a piston which is slidably mounted in the inner cylindrical tube and is attached to the bottom end of the rod.
- the piston divides the internal volume of the inner cylindrical tube into a rebound chamber and a compression chamber, which contain the damping fluid.
- the piston is provided with a first valve assembly comprising a pair of non-return valves, namely a compensation valve, which during the compression phase of the shock-absorber adjusts the flow of the damping fluid from the compression chamber to the rebound chamber, and a rebound valve, which during the rebound phase of the shock-absorber adjusts the flow of the damping fluid from the rebound chamber to the compression chamber.
- a second valve assembly is mounted on the bottom of the inner cylindrical tube and comprises a pair of non-return valves, namely a compression valve, which during the compression phase adjusts the flow of the damping fluid from the compression chamber to the reservoir chamber, and an intake valve, which during the rebound phase adjusts the flow of the damping fluid from the reservoir chamber to the compression chamber.
- the non-return valves of the first valve assembly, as well as those of the second valve assembly are made as passive valves.
- This known shock-absorber further comprises first and second electronically-controlled valves arranged to adjust the flow of the damping fluid during the rebound phase and during the compression phase, respectively. More specifically, the first electronically-controlled valve is connected on the one hand with the reservoir chamber and on the other with a first intermediate chamber defined between the inner cylindrical tube and a first intermediate cylindrical tube which is radially interposed between the inner cylindrical tube and the outer cylindrical tube, said first intermediate chamber being permanently in fluid communication with the rebound chamber. The first electronically-controlled valve is arranged to adjust, during the rebound phase, the flow of the damping fluid from the rebound chamber to the reservoir chamber via the first intermediate chamber, and hence to adjust the damping force of the shock-absorber during that phase.
- the second electronically-controlled valve is connected on the one hand with the reservoir chamber and on the other with a second intermediate chamber defined between the inner cylindrical tube and a second intermediate cylindrical tube which is radially interposed between the inner cylindrical tube and the outer cylindrical tube, said second intermediate chamber being permanently in fluid communication with the compression chamber.
- the second electronically-controlled valve is arranged to adjust, during the compression phase, the flow of the damping fluid from the compression chamber to the reservoir chamber via the second intermediate chamber, and hence to adjust the damping force of the shock-absorber during that phase.
- the valve bodies of both the electronically-controlled valves of this known shock-absorber are arranged outside the outer cylindrical tube.
- the shock-absorber known from DE 10 2005 053 394 A1 has larger sizes than variable-damping shock-absorbers having only one electronically-controlled valve, and is therefore more difficult to mount on board of a vehicle, in particular where the available space is rather small.
- the shock-absorber known from DE 10 2005 053 394 A1 is characterized by the presence of a non-return valve, which is placed on the bottom of the first intermediate cylindrical tube, hydraulically in parallel with the first electronically-controlled valve, and allows oil flow only in the direction from the reservoir chamber to the rebound chamber via the first intermediate chamber during the compression phase.
- a non-return valve which is placed on the bottom of the first intermediate cylindrical tube, hydraulically in parallel with the first electronically-controlled valve, and allows oil flow only in the direction from the reservoir chamber to the rebound chamber via the first intermediate chamber during the compression phase.
- said non-return valve may be subject to jamming during its opening and closing movements.
- non-return valve requires a larger diameter of the first intermediate cylindrical tube, and therefore a larger diameter of the outer cylindrical tube, which causes an increase in the radial size of the shock-absorber with respect to variable-damping hydraulic shock-absorbers having one electronically-controlled valve only.
- the use of two electronically-controlled valves allows to control the rebound phase and the compression phase of the shock-absorber independently of each other, offers a wider range of adjustment, especially during the compression phase, and also allows a better control of the "high" frequencies (approximately 15 Hz) typical of the vehicle wheels, given that the response of the shock-absorber is very fast by virtue of the possibility to set each electronically-controlled valve in advance, i.e. before the beginning of the respective phase (rebound or compression).
- variable-damping hydraulic shock-absorber having the features defined in the accompanying independent claim 1.
- the invention is based on the idea of providing the hydraulic shock-absorber with first and second electronically-controlled valves configured to control the flow of the damping fluid during the rebound phase only and during the compression phase only, respectively, wherein the first electronically-controlled valve is arranged inside the body of the shock-absorber, being mounted in particular on the piston or on the rod and being thus drivingly connected for translation with the piston and rod assembly, while the second electronically-controlled valve is arranged outside the body of the shock-absorber.
- the hydraulic shock-absorber according to the invention keeps the above-mentioned advantages of the prior art, related to the use of two electronically-controlled valves to control the flow of the damping fluid during the compression and rebound phases, and also has smaller sizes than the prior art, since only one of the two electronically-controlled valves is arranged outside the body of the shock-absorber.
- Figure 1 is an axial section view schematically showing the architecture of a variable-damping hydraulic shock-absorber according to the present invention.
- shock-absorber a variable-damping hydraulic shock-absorber (hereinafter simply referred to as shock-absorber), intended in particular for use in a vehicle suspension, is generally indicated at 10.
- the shock-absorber 10 basically comprises a cylindrical body 12 (hereinafter imply referred to as body) extending along a longitudinal axis x and a rod 14 which partially protrudes (upwards, according to the point of view of a person looking at Figure 1 ) from the body 12 and is movable axially (that is, along the direction of the longitudinal axis x) with respect to the body 12.
- body 12 hereinafter imply referred to as body
- rod 14 which partially protrudes (upwards, according to the point of view of a person looking at Figure 1 ) from the body 12 and is movable axially (that is, along the direction of the longitudinal axis x) with respect to the body 12.
- the body 12 comprises an inner cylindrical tube 16 and an outer cylindrical tube 18 which are arranged coaxially to each other and enclose a reservoir chamber 20 containing a damping fluid (which is typically oil and therefore will be, for the sake of simplicity, hereinafter referred to as oil) in a lower portion thereof and gas in the remaining upper portion. Said lower and upper portions of the reservoir chamber are indicated at 20a and 20b, respectively.
- a damping fluid which is typically oil and therefore will be, for the sake of simplicity, hereinafter referred to as oil
- a piston 22 is slidably mounted in the inner cylindrical tube 16 and is attached to the bottom end of the rod 14.
- the piston 22 divides the internal volume of the inner cylindrical tube 16 into a rebound chamber 24 and a compression chamber 26, which both contain oil.
- the piston 22 is provided with a first valve assembly comprising a pair of non-return valves 28 and 30, namely a compensation valve 28, which allows oil flow only in the direction from the compression chamber 26 to the rebound chamber 24, and a rebound valve 30, which allows oil flow only in the direction from the rebound chamber 24 to the compression chamber 26.
- a second valve assembly is mounted on the bottom of the inner cylindrical tube 16 and comprises a pair of non-return valves 32 and 34, namely a compression valve 32, which allows oil flow only in the direction from the compression chamber 26 to the reservoir chamber 20, and an intake valve 34, which allows oil flow only in the direction from the reservoir chamber 20 to the compression chamber 26.
- the non-return valves 28 and 30 of the first valve assembly, as well as the non-return valves 32 and 34 of the second valve assembly, are made as passive valves.
- an intermediate cylindrical tube 36 is arranged around the inner cylindrical tube 16, coaxially thereto, and encloses, along with the inner cylindrical tube 16, an intermediate chamber 38.
- the intermediate chamber 38 is permanently in fluid communication with the compression chamber 26.
- the shock-absorber 10 further comprises a first electronically-controlled valve 40 and a second electronically-controlled valve 42, hereinafter simply referred to as first and second electronic valves, respectively.
- the first electronic valve 40 is preferably made as a two-way solenoid valve and basically comprises, in per-se-known manner, a valve body 44, a closure member 46 movable relative to the valve body 44 and a solenoid 48 arranged to control the movement of the closure member 46 to adjust the oil flow through either way of the valve.
- the solenoid 48 is supplied by an electric wire 49 extending along the longitudinal axis x through the rod 14 (which, for this purpose, is made as a hollow rod).
- the second electronic valve 42 is preferably made as a two-way solenoid valve and basically comprises, in per-se-known manner, a valve body 50, a closure member 52 movable relative to the valve body 50 and a solenoid 54 arranged to control the movement of the closure member 52 to adjust the oil flow through either way of the valve.
- the solenoid 54 is supplied by an electric wire 55.
- the two electronic valves 40 and 42 may be piloted or double-stage valves. It is, in fact, clear that the present invention is not limited to the use of a particular type of electronic valve.
- the first and second electronic valves 40 and 42 may be made both as continuously-controlled proportional valves or both as ON/OFF valves. It may also be envisaged that one of the two valves is a continuously-controlled proportional valve and the other one is an ON/OFF valve.
- the first electronic valve 40 is arranged inside the body 12 of the shock-absorber. More specifically, the first electronic valve 40 is arranged inside the inner cylindrical tube 16, so as to be drivingly connected for translation along the longitudinal axis x with the assembly formed by the rod 14 and the piston 22. In the embodiment schematically shown in Figure 1 , the first electronic valve 40 is mounted on the rod 14, but may alternatively be mounted on the piston 22.
- the first electronic valve 40 controls oil flow from the rebound chamber 24 to the compression chamber 26, along a bypass conduit 56 that extends through the piston 22, during the rebound phase of the shock-absorber, working in parallel to the non-return valves 28 and 30 of the first valve assembly provided on the piston 22.
- the first electronic valve 40 is therefore connected at its first way with the rebound chamber 24 and at its second way with the bypass conduit 56.
- the second electronic valve 42 is instead arranged outside the body 12 of the shock-absorber. More specifically, the second electronic valve 42 is arranged outside the outer cylindrical tube 18.
- the second electronic valve 42 controls oil flow from the compression chamber 26 to the reservoir chamber 20 (in particular to the lower portion 20a of that chamber) via the intermediate chamber 38, during the compression phase of the shock-absorber, working in parallel to the non-return valves 32 and 34 of the second valve assembly provided on the bottom of the inner cylindrical tube 16. To this end, the second electronic valve 42 is connected at its first way with the intermediate chamber 38 (and, via that chamber, with the compression chamber 26) and at its second way with the reservoir chamber 20.
- shock-absorber 10 operates as follows.
- the oil flow from the rebound chamber 24 to the compression chamber 26 takes place through the first electronic valve 40 and/or the rebound valve 30, which operate in parallel to each other, while the compensation valve 28 remains closed.
- the oil flow from the reservoir chamber 20 to the compression chamber 26 takes place through the second electronic valve 42 and/or the intake valve 34, while the compression valve 32 remains closed.
- the intake valve 34 has a very soft setting, so as to determine a substantially null pressure drop between the reservoir chamber 20 and the compression chamber 26 and thus remain substantially open during the entire rebound phase. Accordingly, the entire oil flow from the reservoir chamber 20 to the compression chamber 26 passes through the intake valve 34, rather than through the second electronic valve 42 that is arranged hydraulically in parallel thereto. Therefore, the second electronic valve 42 does not have substantially any effect on the behaviour of the shock-absorber 10 during the rebound phase, irrespective of the value of the current command applied to the solenoid 54.
- the oil flow from the compression chamber 26 to the reservoir chamber 20 takes place through the second electronic valve 42 and/or the compression valve 32, which operate in parallel to each other, while the intake valve 34 remains closed.
- the oil flow from the compression chamber 26 to the rebound chamber 24 takes place through the first electronic valve 40 and/or the compensation valve 28, while the rebound valve 30 remains closed.
- the compensation valve 28 has a very soft setting, so as to determine a substantially null pressure drop between the compression chamber 26 and the rebound chamber 24 and thus remain substantially open during the entire compression phase. Accordingly, the entire oil flow from the compression chamber 26 to the rebound chamber 24 passes through the compensation valve 28, rather than through the first electronic valve 40 that is arranged hydraulically in parallel thereto. Therefore, the first electronic valve 40 does not have substantially any effect on the behaviour of the shock-absorber 10 during the compression phase, irrespective of the value of the current command applied to the solenoid 48.
- the electronic valves 40 and 42 may be both made as non-return valves (in particular, as a valve allowing oil flow only in the direction from the rebound chamber 24 to the compression chamber 26, insofar as the first electronic valve 40 is concerned, and as a valve allowing oil flow only in the direction from the compression chamber 26 to the reservoir chamber 20, insofar as the second electronic valve 42 is concerned), since during the compression phase there is no need for the oil flowing from the compression chamber 26 to the rebound chamber 24 to pass through the first electronic valve 40, while during the rebound phase there is no need for the oil flowing from the reservoir chamber 20 to the compression chamber 26 to pass through the second electronic valve 42.
- the shock-absorber according to the invention allows to control the rebound phase and the compression phase independently of each other, due to the fact that it is provided with two electronic valves: in fact, one of the two valves (in the present case, the first electronic valve 40) controls the rebound phase, while the other valve (in the present case, the second electronic valve 42) controls the compression phase.
- having two electronic valves allows a better control of the high frequencies typical of the movements of the vehicle wheels (approximately 15 Hz): the response of the shock-absorber will be, in fact, very fast, since it will be possible to set each of the two electronic valves in advance, i.e. before the beginning of the respective phase (rebound or compression).
- a shock-absorber according to the present invention has smaller sizes than the above-discussed prior art, given that only one of the two electronic valves is arranged outside the body of the shock-absorber and that in the present configuration there is no need to use an annular non-return valve to allow oil flow from the reservoir chamber to the rebound chamber during the compression phase.
- This makes it possible to use the shock-absorber even in applications characterized by a reduced available space, in which applications a shock-absorber according to the above-discussed prior art could not be used due to its large sizes.
- a further advantage over the above-discussed prior art is the reduction in the unsprung masses (i.e. in the masses that move along with the vehicle wheels), since only one electronic valve is mounted on the body of the shock-absorber, and is thus an unsprung mass (the other electronic valve, on the other hand, is mounted on the rod and is thus a sprung mass), and since the shock-absorber comprises one intermediate cylindrical tube only, instead of the two intermediate cylindrical tubes that are provided for in the known shock-absorber discussed above.
- a reduction in the unsprung masses allows to improve the dynamic behaviour of the vehicle.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Fluid-Damping Devices (AREA)
Claims (6)
- Amortisseur hydraulique à amortissement variable, comprenant un corps cylindrique (12) s'étendant le long d'un axe longitudinal (x) et une tige (14) partiellement saillante depuis le corps (12) et mobile axialement par rapport au corps (12),dans lequel le corps (12) comprend un tube cylindrique intérieur (16) et un tube cylindrique extérieur (18) qui renferment une chambre de réservoir (20) contenant un fluide d'amortissement,dans lequel l'amortisseur (10) comprend en outre un piston (22) qui est monté de manière à pouvoir coulisser dans le tube cylindrique intérieur (16), est raccordé à l'extrémité de fond de la tige (14) et divise le volume interne du tube cylindrique intérieur (16) en une chambre de rebond (24) et une chambre de compression (26), qui sont toutes les deux remplies du fluide d'amortissement,dans lequel le corps (12) comprend en outre un tube cylindrique intermédiaire (36) qui est agencé autour du tube cylindrique intérieur (16) et renferme, avec celui-ci, une chambre intermédiaire (38), ladite chambre intermédiaire (38) étant constamment en communication fluidique avec la chambre de compression (26),dans lequel l'amortisseur (10) comprend en outre une première vanne à commande électronique (40) et une seconde vanne à commande électronique (42) qui sont agencées pour ajuster l'écoulement du fluide d'amortissement entre la chambre de rebond (24) et la chambre de compression (26), ainsi qu'entre la chambre de compression (26) et la chambre de réservoir (20), respectivement au cours de la phase de rebond et de la phase de compression, et dans lequel ladite seconde vanne à commande électronique (42) est agencée à l'extérieur du corps (12) de l'amortisseur (10) et est reliée hydrauliquement d'une part à la chambre de réservoir (20) et d'autre part à la chambre intermédiaire (38) pour ajuster, au cours de la phase de compression, l'écoulement du fluide d'amortissement depuis la chambre de compression (26) jusqu'à la chambre de réservoir (20) via la chambre intermédiaire (38),caractérisé en ce que ladite premier vanne à commande électronique (40) est agencée à l'intérieur du corps (12) de l'amortisseur (10), en l'occurrence à l'intérieur du tube cylindrique intérieur (16), de manière à être reliée par entraînement à la tige (14) pour une translation le long de l'axe longitudinal (x), et est reliée hydrauliquement d'une part la chambre de rebond (24) et d'autre part à la chambre de compression (26) pour ajuster, au cours de la phase de rebond, l'écoulement du fluide d'amortissement depuis la chambre de rebond (24) jusqu'à la chambre de compression (26).
- Amortisseur hydraulique selon la revendication 1, dans lequel ladite première vanne à commande électronique (40) est une vanne proportionnelle à commande continue ou une vanne marche/arrêt.
- Amortisseur hydraulique selon la revendication 1 ou 2, dans lequel ladite seconde vanne à commande électronique (42) est une vanne proportionnelle à commande continue ou une vanne marche/arrêt.
- Amortisseur hydraulique selon l'une quelconque des revendications précédentes, dans lequel le piston (22) est pourvu d'un premier ensemble de vannes comprenant une paire de première vannes antiretour (28, 30), en l'occurrence une vanne de compensation (28), qui permet l'écoulement du fluide d'amortissement uniquement dans la direction depuis la chambre de compression (26) jusqu'à la chambre de rebond (24), et une vanne de rebond (30), qui permet l'écoulement du fluide d'amortissement uniquement dans la direction depuis la chambre de rebond (24) jusqu'à la chambre de compression (26), et dans lequel un second ensemble de vannes est monté sur le fond du tube cylindrique intérieur (16) et comprend une paire de secondes vannes antiretour (32, 34), en l'occurrence une vanne de compression (32), qui permet l'écoulement du fluide d'amortissement uniquement dans la direction depuis la chambre de compression (26) jusqu'à la chambre de réservoir (20), et une vanne d'admission (34), qui permet l'écoulement du fluide d'amortissement uniquement dans la direction depuis la chambre de réservoir (20) jusqu'à la chambre de compression (26), lesdites première et seconde vannes antiretour (28, 30, 32, 34) étant des vannes passives.
- Amortisseur hydraulique selon la revendication 4, dans lequel la vanne d'admission (34) est configurée pour rester ouverte pendant toute la phase de rebond, de telle manière que, pendant ladite phase, l'écoulement du fluide d'amortissement depuis la chambre de réservoir (20) jusqu'à la chambre de compression (26) n'intervienne qu'à travers la vanne d'admission (34), au lieu d'intervenir à travers ladite seconde vanne électronique (42).
- Amortisseur hydraulique selon la revendication 4 ou 5, dans lequel la vanne de compensation (28) est configurée pour rester ouverte pendant toute la phase de compression, de telle manière que, pendant ladite phase, l'écoulement du fluide d'amortissement depuis la chambre de compression (26) jusqu'à la chambre de rebond (24) n'intervienne qu'à travers la vanne de compensation (28), au lieu d'intervenir à travers ladite première vanne électronique (40).
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
IT102018000007584A IT201800007584A1 (it) | 2018-07-27 | 2018-07-27 | Ammortizzatore idraulico a smorzamento variabile, particolarmente per sospensione di veicolo. |
PCT/IB2019/056386 WO2020021500A1 (fr) | 2018-07-27 | 2019-07-26 | Amortisseur hydraulique à amortissement variable pour suspension de véhicule |
Publications (2)
Publication Number | Publication Date |
---|---|
EP3830444A1 EP3830444A1 (fr) | 2021-06-09 |
EP3830444B1 true EP3830444B1 (fr) | 2022-10-26 |
Family
ID=63965820
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP19758811.4A Active EP3830444B1 (fr) | 2018-07-27 | 2019-07-26 | Amortisseur hydraulique à amortissement variable pour suspension de véhicule |
Country Status (6)
Country | Link |
---|---|
US (1) | US11761508B2 (fr) |
EP (1) | EP3830444B1 (fr) |
JP (1) | JP7495925B2 (fr) |
CN (1) | CN112513492B (fr) |
IT (1) | IT201800007584A1 (fr) |
WO (1) | WO2020021500A1 (fr) |
Families Citing this family (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN107939893B (zh) * | 2017-12-29 | 2024-03-15 | 深圳职业技术学院 | 主动悬架系统、减振器以及减振部件 |
WO2020246315A1 (fr) * | 2019-06-05 | 2020-12-10 | 日立オートモティブシステムズ株式会社 | Amortisseur de type à réglage de force d'amortissement |
CN114072596A (zh) * | 2019-06-26 | 2022-02-18 | 日立安斯泰莫株式会社 | 缓冲器 |
CN115875392A (zh) * | 2021-09-29 | 2023-03-31 | 比亚迪股份有限公司 | 车辆减震器以及车辆 |
Family Cites Families (56)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4031989A (en) * | 1975-02-22 | 1977-06-28 | Antonio Giner Blazquez | Double effect hydraulic shock absorber |
DE3231739A1 (de) * | 1982-08-26 | 1984-03-01 | Fichtel & Sachs Ag, 8720 Schweinfurt | Zweirohr-schwingungsdaempfer oder federbein mit veraenderbarer daempfkraft |
DE3816102C1 (fr) * | 1988-05-11 | 1989-07-13 | Boge Ag, 5208 Eitorf, De | |
DE3925470C2 (de) * | 1988-08-02 | 1996-04-18 | Atsugi Motor Parts Co Ltd | Stoßdämpfer mit einer Dämpfungsventilkonstruktion mit einer innerhalb eines großen Bereichs variablen Dämpfungscharakteristik |
US5222759A (en) * | 1990-02-27 | 1993-06-29 | Robert Bosch Gmbh | Apparatus for active control of body motions in motor vehicles |
DE4007261A1 (de) * | 1990-03-08 | 1991-09-12 | Boge Ag | Regelbarer schwingungsdaempfer |
JPH0454339A (ja) * | 1990-06-20 | 1992-02-21 | Tokico Ltd | 減衰力可変式油圧緩衝器 |
DE4105771A1 (de) * | 1991-02-23 | 1992-08-27 | Boge Ag | Hydraulischer, verstellbarer schwingungsdaempfer fuer kraftfahrzeuge |
DE4132262A1 (de) * | 1991-09-27 | 1993-04-01 | Teves Gmbh Alfred | Hydraulischer regelbarer schwingungsdaempfer fuer kraftfahrzeuge |
US5375683A (en) * | 1992-01-17 | 1994-12-27 | August Bilstein Gmbh & Co. Kg | Controllable vibration damper for motor vehicles |
JP3280725B2 (ja) * | 1992-12-02 | 2002-05-13 | オーリンス レーシング アクティエ ボラーグ | 筒型ショックアブソーバ |
US5586627A (en) * | 1993-05-20 | 1996-12-24 | Tokico, Ltd. | Hydraulic shock absorber of damping force adjustable type |
JP3306526B2 (ja) * | 1993-05-20 | 2002-07-24 | トキコ株式会社 | 減衰力調整式油圧緩衝器 |
ES2123382B1 (es) * | 1994-06-24 | 1999-08-01 | Fichtel & Sachs Ag | Dispositivo para la amortiguacion de sistemas elasticos de suspension de rueda. |
ES2176274T3 (es) * | 1994-12-03 | 2002-12-01 | Zf Sachs Ag | Amortiguador de vibraciones con fuerza de amortiguacion ajustable. |
US5588510A (en) * | 1995-09-25 | 1996-12-31 | Husco International, Inc. | Variable damping force shock absorber |
JP3346221B2 (ja) * | 1997-05-20 | 2002-11-18 | 三菱自動車工業株式会社 | ショックアブソーバ |
JPH1130264A (ja) * | 1997-07-09 | 1999-02-02 | Unisia Jecs Corp | 減衰特性可変型緩衝器 |
DE10020778B4 (de) * | 1999-04-28 | 2005-01-13 | Tokico Ltd., Kawasaki | Hydraulischer Stossdämpfer mit Dämpfungskraftregelung |
US6464048B1 (en) * | 2000-07-24 | 2002-10-15 | Tenneco Automotive Inc. | Solenoid actuated continuously variable shock absorber |
JP2002070921A (ja) * | 2000-09-01 | 2002-03-08 | Tokico Ltd | 減衰力調整式油圧緩衝器 |
US6668986B2 (en) * | 2002-01-08 | 2003-12-30 | Delphi Technologies, Inc. | Active hydraulic fluid vehicular suspension damper |
US20030192755A1 (en) * | 2002-04-16 | 2003-10-16 | Barbison James M. | Shock absorber with toroidal solenoid adjustable damping |
US6926128B2 (en) * | 2003-06-10 | 2005-08-09 | Arvin Technologies, Inc. | Adaptive shock damping control |
US7438164B2 (en) * | 2003-12-08 | 2008-10-21 | Tenneco Automotive Operating Company Inc. | Solenoid actuated continuously variable servo valve for adjusting damping in shock absorbers and struts |
DE102005053394B4 (de) * | 2004-11-11 | 2018-04-26 | Zf Friedrichshafen Ag | Schwingungsdämpfer mit verstellbarer Dämpfkraft |
DE102004054474B3 (de) * | 2004-11-11 | 2006-06-08 | Zf Friedrichshafen Ag | Schwingungsdämpfer mit verstellbarer Dämpfkraft |
DE202005011439U1 (de) * | 2005-07-18 | 2006-11-23 | Hemscheidt Fahrwerktechnik Gmbh & Co. Kg | Federungseinrichtung für Kraftfahrzeuge |
DE102005048949B3 (de) * | 2005-10-13 | 2006-12-14 | Zf Friedrichshafen Ag | Schwingungsdämpfer mit verstellbarer Dämpfkraft |
US7926632B2 (en) * | 2007-04-16 | 2011-04-19 | Tenneco Automotive Operating Company Inc. | Shock absorber having a continuously variable valve with base line valving |
US7950506B2 (en) * | 2007-07-31 | 2011-05-31 | Tenneco Automotive Operating Company Inc. | Semi third tube design |
JP5212794B2 (ja) * | 2008-04-25 | 2013-06-19 | 日立オートモティブシステムズ株式会社 | シリンダ装置及びこれを用いたスタビライザ装置。 |
KR100977191B1 (ko) * | 2010-02-22 | 2010-08-23 | 주식회사 케이. 아이. 씨 | 감쇠력 조절가능한 쇽업쇼바 |
WO2012006294A1 (fr) * | 2010-07-05 | 2012-01-12 | Fluid Ride Ltd. | Jambe de suspension pour véhicule |
IT1401610B1 (it) * | 2010-08-04 | 2013-07-26 | Sistemi Sospensioni Spa | Pistone per ammortizzatore a smorzamento variabile, particolarmente per sospensione di veicolo, provvisto di quattro valvole passive di controllo del flusso e di un'elettrovalvola di ripartizione del flusso. |
CN102168732B (zh) * | 2010-12-15 | 2012-11-28 | 长春孔辉汽车科技有限公司 | 半主动减振器 |
DE102011100307A1 (de) * | 2011-05-03 | 2012-11-08 | Daimler Ag | Landgebundenes Personenkraftfahrzeug mit einer Entkopplungsvorrichtung sowie Verfahren zum Entkoppeln einer Karosserie des landgebundenen Personenkraftfahrzeugs |
US9062737B2 (en) * | 2012-06-04 | 2015-06-23 | Mclaren Automotive Limited | Shock absorber with four chambers |
JP5731453B2 (ja) * | 2012-08-24 | 2015-06-10 | カヤバ工業株式会社 | ダンパ |
JP6134957B2 (ja) * | 2012-09-28 | 2017-05-31 | 日立オートモティブシステムズ株式会社 | 緩衝器 |
JP2014122656A (ja) * | 2012-12-20 | 2014-07-03 | Yamaha Motor Hydraulic System Co Ltd | ショックアブソーバ |
JP2014144733A (ja) * | 2013-01-30 | 2014-08-14 | Toyota Motor Corp | 液圧式ショックアブソーバ |
CN105026788B (zh) * | 2013-02-28 | 2018-05-04 | 坦尼科汽车操作有限公司 | 带有集成电子设备的阻尼器 |
KR101728266B1 (ko) * | 2013-03-22 | 2017-04-18 | 케이와이비 가부시키가이샤 | 완충 장치 |
KR101771690B1 (ko) * | 2013-05-14 | 2017-08-25 | 주식회사 만도 | 로드 가이드에 설치된 부가밸브를 갖는 감쇠력 가변식 쇽업소버 |
KR101761868B1 (ko) * | 2013-08-14 | 2017-07-26 | 주식회사 만도 | 듀얼 솔레노이드 밸브 구조의 감쇠력 가변식 쇽업소버 |
DE102014208367B4 (de) * | 2014-05-05 | 2022-10-27 | Zf Friedrichshafen Ag | Dämpfventileinrichtung für einen Schwingungsdämpfer |
JP6434869B2 (ja) * | 2015-07-13 | 2018-12-05 | Kyb株式会社 | 減衰弁および緩衝器 |
JP6514608B2 (ja) * | 2015-09-02 | 2019-05-15 | Kyb株式会社 | 緩衝装置 |
KR102471853B1 (ko) * | 2015-10-22 | 2022-11-30 | 에이치엘만도 주식회사 | 감쇠력 가변식 쇽업소버 |
CN206000927U (zh) * | 2016-09-13 | 2017-03-08 | 常熟理工学院 | 比例电磁铁式汽车减震器用调节阀总成 |
DE102016219117B4 (de) * | 2016-09-30 | 2022-02-24 | Thyssenkrupp Ag | Schwingungsdämpfer für ein Kraftfahrzeug und ein Verfahren zum Herstellen einer Presspassung zwischen einem Dämpferinnenrohr und mindestens einer Trennscheibe |
US10393210B2 (en) * | 2016-11-18 | 2019-08-27 | Beijingwest Industries Co., Ltd. | Dual mode hydraulic damper |
IT201700006900A1 (it) * | 2017-01-23 | 2018-07-23 | Sistemi Sospensioni Spa | Attuatore lineare idraulico con sistema di bloccaggio atto a bloccare il movimento di compressione dell'attuatore. |
WO2018216716A1 (fr) * | 2017-05-26 | 2018-11-29 | 日立オートモティブシステムズ株式会社 | Amortisseur |
DE102019108070A1 (de) * | 2019-03-28 | 2020-10-01 | Thyssenkrupp Ag | Schwingungsdämpfer und Fahrzeug |
-
2018
- 2018-07-27 IT IT102018000007584A patent/IT201800007584A1/it unknown
-
2019
- 2019-07-26 US US17/263,657 patent/US11761508B2/en active Active
- 2019-07-26 CN CN201980050182.4A patent/CN112513492B/zh active Active
- 2019-07-26 JP JP2021504387A patent/JP7495925B2/ja active Active
- 2019-07-26 WO PCT/IB2019/056386 patent/WO2020021500A1/fr unknown
- 2019-07-26 EP EP19758811.4A patent/EP3830444B1/fr active Active
Also Published As
Publication number | Publication date |
---|---|
IT201800007584A1 (it) | 2020-01-27 |
JP7495925B2 (ja) | 2024-06-05 |
JP2021531441A (ja) | 2021-11-18 |
CN112513492B (zh) | 2022-10-11 |
US11761508B2 (en) | 2023-09-19 |
CN112513492A (zh) | 2021-03-16 |
US20210310535A1 (en) | 2021-10-07 |
WO2020021500A1 (fr) | 2020-01-30 |
EP3830444A1 (fr) | 2021-06-09 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
EP3830444B1 (fr) | Amortisseur hydraulique à amortissement variable pour suspension de véhicule | |
KR102588313B1 (ko) | 감쇠력을 조정할 수 있는 진동 댐퍼 | |
US7950506B2 (en) | Semi third tube design | |
EP3039312B1 (fr) | Amortisseur de chocs à soupape dépendant de la fréquence | |
US8511447B2 (en) | Triple tube shock absorber having a shortened intermediate tube | |
US20200011395A1 (en) | Damper with dual springs | |
US9994239B2 (en) | Vehicle with force-controlled shock absorber (2-pipe shock absorber) | |
US20130081913A1 (en) | Welding of transfer ring on round tube | |
EP1983213A2 (fr) | Absorbeur de chocs à pression fluide réglable de force d'amortissement | |
EP0297194B1 (fr) | Amortisseur variable | |
US4397452A (en) | Hydro-mechanical stop for a shock absorber | |
JP2008089037A (ja) | 減衰力調整式油圧緩衝器 | |
US20210018059A1 (en) | Damper with dual pistons | |
JP2019113171A (ja) | 緩衝器 | |
EP3078878B1 (fr) | Amortisseur de chocs | |
JP4748017B2 (ja) | 減衰力調整式油圧緩衝器 | |
US10302169B2 (en) | Hydraulic vibration damper | |
JP2008008471A (ja) | 減衰力調整式油圧緩衝器 | |
GB2161579A (en) | An adjustable single-tube hydraulic damper | |
US11365782B2 (en) | Rotary damper, particularly for vehicle suspension | |
EP1176333A2 (fr) | Amortisseur à variation continue actionné par un soleinoide | |
JPWO2020021500A5 (fr) | ||
EP4170195A1 (fr) | Amortisseur télescopique passif | |
US20230018887A1 (en) | Telescopic passive damper | |
GB2310023A (en) | Hydraulic Damper |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: UNKNOWN |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: THE INTERNATIONAL PUBLICATION HAS BEEN MADE |
|
PUAI | Public reference made under article 153(3) epc to a published international application that has entered the european phase |
Free format text: ORIGINAL CODE: 0009012 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: REQUEST FOR EXAMINATION WAS MADE |
|
17P | Request for examination filed |
Effective date: 20210223 |
|
AK | Designated contracting states |
Kind code of ref document: A1 Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR |
|
DAV | Request for validation of the european patent (deleted) | ||
DAX | Request for extension of the european patent (deleted) | ||
GRAP | Despatch of communication of intention to grant a patent |
Free format text: ORIGINAL CODE: EPIDOSNIGR1 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: GRANT OF PATENT IS INTENDED |
|
INTG | Intention to grant announced |
Effective date: 20220323 |
|
GRAS | Grant fee paid |
Free format text: ORIGINAL CODE: EPIDOSNIGR3 |
|
GRAJ | Information related to disapproval of communication of intention to grant by the applicant or resumption of examination proceedings by the epo deleted |
Free format text: ORIGINAL CODE: EPIDOSDIGR1 |
|
GRAL | Information related to payment of fee for publishing/printing deleted |
Free format text: ORIGINAL CODE: EPIDOSDIGR3 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: REQUEST FOR EXAMINATION WAS MADE |
|
INTC | Intention to grant announced (deleted) | ||
GRAP | Despatch of communication of intention to grant a patent |
Free format text: ORIGINAL CODE: EPIDOSNIGR1 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: GRANT OF PATENT IS INTENDED |
|
GRAA | (expected) grant |
Free format text: ORIGINAL CODE: 0009210 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: THE PATENT HAS BEEN GRANTED |
|
INTG | Intention to grant announced |
Effective date: 20220901 |
|
AK | Designated contracting states |
Kind code of ref document: B1 Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR |
|
REG | Reference to a national code |
Ref country code: GB Ref legal event code: FG4D |
|
REG | Reference to a national code |
Ref country code: CH Ref legal event code: EP |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R096 Ref document number: 602019021155 Country of ref document: DE |
|
REG | Reference to a national code |
Ref country code: AT Ref legal event code: REF Ref document number: 1527231 Country of ref document: AT Kind code of ref document: T Effective date: 20221115 |
|
REG | Reference to a national code |
Ref country code: IE Ref legal event code: FG4D |
|
REG | Reference to a national code |
Ref country code: LT Ref legal event code: MG9D |
|
REG | Reference to a national code |
Ref country code: NL Ref legal event code: MP Effective date: 20221026 |
|
REG | Reference to a national code |
Ref country code: AT Ref legal event code: MK05 Ref document number: 1527231 Country of ref document: AT Kind code of ref document: T Effective date: 20221026 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: NL Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20221026 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: SE Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20221026 Ref country code: PT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20230227 Ref country code: NO Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20230126 Ref country code: LT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20221026 Ref country code: FI Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20221026 Ref country code: ES Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20221026 Ref country code: AT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20221026 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: RS Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20221026 Ref country code: PL Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20221026 Ref country code: LV Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20221026 Ref country code: IS Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20230226 Ref country code: HR Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20221026 Ref country code: GR Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20230127 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R097 Ref document number: 602019021155 Country of ref document: DE |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: SM Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20221026 Ref country code: RO Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20221026 Ref country code: EE Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20221026 Ref country code: DK Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20221026 Ref country code: CZ Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20221026 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: IT Payment date: 20230620 Year of fee payment: 5 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: SK Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20221026 Ref country code: AL Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20221026 |
|
PLBE | No opposition filed within time limit |
Free format text: ORIGINAL CODE: 0009261 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT |
|
26N | No opposition filed |
Effective date: 20230727 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: SI Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20221026 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: DE Payment date: 20230620 Year of fee payment: 5 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: MC Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20221026 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: MC Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20221026 |
|
REG | Reference to a national code |
Ref country code: CH Ref legal event code: PL |
|
REG | Reference to a national code |
Ref country code: BE Ref legal event code: MM Effective date: 20230731 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: LU Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20230726 |
|
GBPC | Gb: european patent ceased through non-payment of renewal fee |
Effective date: 20230726 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: LU Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20230726 |
|
REG | Reference to a national code |
Ref country code: IE Ref legal event code: MM4A |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: CH Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20230731 Ref country code: GB Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20230726 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: BE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20230731 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: IE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20230726 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: IE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20230726 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: FR Payment date: 20240619 Year of fee payment: 6 |